EP0483602B1 - Sicherheitsventil - Google Patents

Sicherheitsventil Download PDF

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Publication number
EP0483602B1
EP0483602B1 EP91117675A EP91117675A EP0483602B1 EP 0483602 B1 EP0483602 B1 EP 0483602B1 EP 91117675 A EP91117675 A EP 91117675A EP 91117675 A EP91117675 A EP 91117675A EP 0483602 B1 EP0483602 B1 EP 0483602B1
Authority
EP
European Patent Office
Prior art keywords
seat
safety valve
valve according
seat bushing
bushing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP91117675A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0483602A1 (de
Inventor
Hans-Peter Dipl.-Ing. Schabert
Alfons Dipl.-Ing. Jezussek
Willi Dipl.-Ing. Stecher
Benedikt Dipl.-Ing. Wintermann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG, Siemens Corp filed Critical Siemens AG
Publication of EP0483602A1 publication Critical patent/EP0483602A1/de
Application granted granted Critical
Publication of EP0483602B1 publication Critical patent/EP0483602B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/08—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for providing a large discharge passage
    • F16K17/082—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for providing a large discharge passage with piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/0433—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with vibration preventing means

Definitions

  • the invention relates to a safety valve according to the preamble of the main claim.
  • the increase in leakage caused by the cooling effect of the expanding leakage steam occurs in particular in the case of high-lift safety valves, as described in particular in the TÜV manual 1 "Pipelines in Power Plants", TÜV Rheinland, Cologne 1978, p. 47, FIG. 42, cf.
  • the preamble of claim 1 are known.
  • the sealing seat is surrounded by a tubular deflecting body, which deflects the steam blown off when activated into a flow directed along the outside of the seat bushing in order to generate an additional force component on the spring-loaded closure piece to increase the stroke.
  • This deflecting body also acts on any leakage steam flow and also leads it to the outside of the valve seat bushing.
  • the leakage vapor cooled by expansion causes cooling with thermal changes in shape that reinforce the initial leak.
  • the cooling effect of the escaping steam is particularly pronounced in high-lift safety valves for the primary circuit of pressurized water reactors, because the throttled relaxation on the saturated steam line begins at around 175 bar and at ambient pressure in the ends in the wet steam area.
  • the cooling effect is further intensified by the moisture content in the leak steam.
  • a valve arrangement is known from US Pat. No. 4,130,130, in which the seat bushing of a valve is surrounded by a sleeve.
  • This sleeve is located on an internal thread close to the circumference of the upper end of the seat bushing of the valve, the seat surface of which it projects.
  • this sleeve does have a significant influence on the flow in the region of the seat surface of the valve, but on the other hand the sleeve is thermally closely coupled to the valve via the thread on the seat bushing of the valve.
  • the invention is based on the object of specifying a safety valve for water vapor in which an increase in the leakage is largely avoided even when small leaks occur.
  • the stated object is achieved according to the invention with the features of the main claim.
  • the thermal insulation of the outside of the seat bushing from the flow channel reduces the cooling effect which is exerted directly on the seat bushing and the mechanical change in shape of the seat bushing in the region of the sealing seat is limited.
  • the thermal insulation of the seat bushing is particularly advantageous in the case of a high-lift safety valve with a flow channel, which is formed by a deflecting body surrounding the seat bushing in the region of its seat surface and which converts the steam emerging at the seat surface into a flow with a flow component directed parallel to the longitudinal axis of the seat bushing redirects.
  • the seat bushing is surrounded by an insulating sleeve at least in the region of the flow channel.
  • the insulating sleeve can be made of the same material as the seat bushing. Since the insulating sleeve and the seat bushing are separate parts, a noticeable reduction in the heat transfer to the seat bushing is guaranteed even when the insulating sleeve fits snugly on the seat bushing, but an air gap is provided between the insulating sleeve and the seat bushing to increase the thermal insulation. This air gap is preferably separated from the flow channel by a sealing lip.
  • this sealing lip is formed by a collar on the inner edge of the insulating sleeve.
  • the wall thickness of the insulating sleeve in the area of the sealing lip is smaller than in the rest of the area and in particular less than half the wall thickness of the seat bushing at its end facing the closure piece. This results in a resilient seat of the sealing lip on the outer circumference of the seat bushing and thus an increased sealing effect.
  • the closure piece is also provided with a thermally insulating cap and is protected by this from the cooling effect of the leakage vapor.
  • the risk of leakage increased due to thermal contraction of the seat bushing is particularly reduced if the seat bushing in its area facing the valve seat has the shape of a hollow cylinder, the height of which is at least about 0.6 times the inside diameter and the wall thickness of which is less than 0. Is 2 times its inner diameter.
  • the hollow cylindrical part preferably merges into a base body with a transition radius that is greater than the wall thickness.
  • the seat bushing preferably consists of a material with a low coefficient of thermal expansion, in particular of ferritic stainless steel with a chromium content of 13 to 17%.
  • a high-lift safety valve for water vapor contains a spring-loaded piston 2, which is guided in a sliding bush 4 and receives a closure piece 6, which in the closed state is pressed with its seat 8 against the seat 10 of a seat bush 12.
  • the seat bushing 12 comprises a base body 16, over which a hollow cylindrical part 14 projects.
  • This hollow cylindrical part 14 carries the seat surface 10 on its end face facing the closure piece 6 and is surrounded by an insulating sleeve 20 which extends up to this end face.
  • the insulating sleeve 20 consists of stainless steel and is embedded in a hollow cylindrical recess in the base body 16 of the seat bushing 12 and fixed there with locking pins, not shown in the figure.
  • the seat bushing 12 and the insulating sleeve 20 are surrounded by a hollow cylindrical deflecting body 18, which is formed by a tubular extension of the sliding bushing 4.
  • a hollow cylindrical flow channel 19 is formed between the deflecting body 18 and the insulating sleeve 20.
  • the essentially radially escaping steam between the seat surfaces 8 and 10 is deflected by the deflecting body 18 and moves in the flow channel 19 in a flow directed away from the closure piece 6 with a parallel to the longitudinal axis 15 of the seat bushing 12 directed speed component along the outer jacket of the insulating sleeve surrounding the seat bushing 12 20.
  • the high lift safety valve is shown in a closed state.
  • the seat bushing 12 is thermally insulated from the flow channel 19 by the insulating sleeve 20, so that the leakage steam escaping from the seat surfaces 8 and 10 practically does not come into contact with the outer jacket of the seat bushing 12.
  • the steam cooled by isenthalpic expansion for example from 175 bar to 1 bar, cannot therefore develop its cooling effect directly on the seat bushing 12.
  • the heat transfer to the seat bushing 12 is reduced by the insulating sleeve 20 and the extent of the mechanical deformations of the seat bushing 12 in the region of the seat surface 10 is limited.
  • the hollow cylindrical part 14 of the seat bushing 12 is long and thin-walled and made of a material with a low coefficient of thermal expansion and low thermal conductivity, for example made of steel with 13-17% chromium content.
  • the seat bushing 12 becomes elastic, so that the local axial shrinkage associated with the local hypothermia is smaller than the elastic compression of the hollow cylindrical part 14 of the seat bushing 12 in the axial direction, which is generated by the excess force of the valve spring due to the internal pressure-dependent piston force. This measure prevents an increase in the leakage rate caused by a small local cooling which cannot be avoided even when using an insulating sleeve.
  • the wall thickness d is at least 0.6 D, preferably more than 1.5 D.
  • the wall thickness d is approximately 2.5 mm in a particularly favorable embodiment.
  • an ample radius R is used to avoid notch stresses, which is preferably greater than d.
  • an air gap 21 of width s can be seen between the insulating sleeve 20 and the hollow cylindrical part 14 of the seat bushing 12.
  • This width s is greater than 0.02 mm, preferably greater than 0.10 mm.
  • the insulating sleeve 20 is provided with a sealing lip 22 in the form of an inner collar, which is positively connected to the outer wall of the seat bushing 12. This sealing lip 22 prevents escaping wet steam from entering the hollow cylindrical gap 21.
  • the insulating sleeve 20 is thinner in its area facing the seat surface 10 than in the rest of the area and has a wall thickness a there that is preferably less than half the wall thickness d of the hollow cylindrical part 14 of the seat bushing 12. This enables the sealing lip 22 to have a resilient fit on the outer circumference the seat bushing 12 and a good seal of the air gap 21. In addition, local cooling of the insulating sleeve 20 in the region of the sealing lip 22 causes a radial contraction of the insulating sleeve 20, so that the effectiveness of the sealing is improved without undue radial forces being exerted on the seat bushing 12 become.
  • the seat bushing 12 is provided in the area of the seat surface 10 on the outer circumference with a recess which extends up to the outer circumference of the seat surface 10.
  • the insulating sleeve 20 is there around the seat bushing 12 pulled around, so that there is a sealing lip 24, which covers almost the entire front area of the seat bushing 12 except for the seat surface 10 and protects against cooling. This results in particularly good thermal insulation of the seat bushing 12.
  • the closure piece 6 is thermally insulated on its outer surface by a cap 30. Air gaps, not shown in the figure, can also be provided between the cap 30 and the closure piece 6.
  • the cap 30 also protects the closure piece from being cooled by leakage steam. These measures reduce a thermal contraction or warping of the closure piece in the region of the end face which reduces the sealing effect.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Lift Valve (AREA)
  • Details Of Valves (AREA)
EP91117675A 1990-10-30 1991-10-16 Sicherheitsventil Expired - Lifetime EP0483602B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4034531A DE4034531C1 (enrdf_load_stackoverflow) 1990-10-30 1990-10-30
DE4034531 1990-10-30

Publications (2)

Publication Number Publication Date
EP0483602A1 EP0483602A1 (de) 1992-05-06
EP0483602B1 true EP0483602B1 (de) 1995-05-31

Family

ID=6417332

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91117675A Expired - Lifetime EP0483602B1 (de) 1990-10-30 1991-10-16 Sicherheitsventil

Country Status (3)

Country Link
EP (1) EP0483602B1 (enrdf_load_stackoverflow)
DE (2) DE4034531C1 (enrdf_load_stackoverflow)
ES (1) ES2072510T3 (enrdf_load_stackoverflow)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4424724C2 (de) * 1994-07-13 1996-07-04 Siemens Ag Steuerventil
DE10350914A1 (de) * 2003-10-31 2005-06-09 Hydac Technology Gmbh Ventil, insbesondere Gassicherheitsventil

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB663333A (en) * 1949-09-08 1951-12-19 Manning Maxwell & Moore Improvements in or relating to safety valves
US2643671A (en) * 1952-06-21 1953-06-30 Manning Maxwell & Moore Inc Spring loaded pop-safety valve
FR1159335A (fr) * 1956-10-15 1958-06-26 Le Clapet Hoerbiger Soupape de sûreté perfectionnée
US3282289A (en) * 1964-09-28 1966-11-01 Bendix Corp Hot gas relief valve
US3425444A (en) * 1966-01-10 1969-02-04 Henry Valve Co Relief valve
GB1164678A (en) * 1966-12-27 1969-09-17 Toa Valve Company Ltd Improvements relating to Pop Safety Valves
US4130130A (en) * 1976-11-15 1978-12-19 Crosby Valve & Gage Company Valve with variable secondary orifice

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
TÜV-Handbuch 1 " Rohrleitungen in Kraftwerken" , TÜV-Rheinland, Köln 1978, s. 47 *

Also Published As

Publication number Publication date
DE59105620D1 (de) 1995-07-06
EP0483602A1 (de) 1992-05-06
DE4034531C1 (enrdf_load_stackoverflow) 1992-03-05
ES2072510T3 (es) 1995-07-16

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